CN108374870B - Two-stage transmission for electric automobile - Google Patents

Two-stage transmission for electric automobile Download PDF

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Publication number
CN108374870B
CN108374870B CN201711267404.7A CN201711267404A CN108374870B CN 108374870 B CN108374870 B CN 108374870B CN 201711267404 A CN201711267404 A CN 201711267404A CN 108374870 B CN108374870 B CN 108374870B
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China
Prior art keywords
gear
sun gear
brake
planetary
sun
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CN201711267404.7A
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Chinese (zh)
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CN108374870A (en
Inventor
金善显
禹先范
吴世勋
崔德洵
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Neooto Co Ltd
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Neooto Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/58—Gearings having only two central gears, connected by orbital gears with sets of orbital gears, each consisting of two or more intermeshing orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/46—Gearings having only two central gears, connected by orbital gears
    • F16H3/48—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears
    • F16H3/52—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears
    • F16H3/56—Gearings having only two central gears, connected by orbital gears with single orbital gears or pairs of rigidly-connected orbital gears comprising orbital spur gears both central gears being sun gears
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/043—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel
    • B60K17/046—Transmission unit disposed in on near the vehicle wheel, or between the differential gear unit and the wheel with planetary gearing having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K7/00—Disposition of motor in, or adjacent to, traction wheel
    • B60K7/0007—Disposition of motor in, or adjacent to, traction wheel the motor being electric
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/3023—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure
    • F16H63/3026—Constructional features of the final output mechanisms the final output mechanisms comprising elements moved by fluid pressure comprising friction clutches or brakes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K7/00—Disposition of motor in, or adjacent to, traction wheel
    • B60K2007/0061—Disposition of motor in, or adjacent to, traction wheel the motor axle being parallel to the wheel axle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60Y—INDEXING SCHEME RELATING TO ASPECTS CROSS-CUTTING VEHICLE TECHNOLOGY
    • B60Y2200/00—Type of vehicle
    • B60Y2200/90—Vehicles comprising electric prime movers
    • B60Y2200/91—Electric vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two forward speeds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention relates to a two-stage transmission for an electric vehicle, comprising a first sun gear; a second sun gear; a plurality of first planetary gears that mesh with the first sun gear to rotate or revolve in a circumferential direction of the first sun gear; a ring gear including an inner peripheral gear and an outer peripheral gear, the outer peripheral gear being engaged with an input gear rotated by a driving device to rotate; a plurality of second planetary gears that are meshed with the inner peripheral gear and the second sun gear and that rotate or revolve in the circumferential direction of the second sun gear; a carrier for rotatably coupling the first planetary gear and the second planetary gear; and a brake unit for selectively fixing the first sun gear and the second sun gear.

Description

Two-stage transmission for electric automobile
Technical Field
The present invention relates to a two-stage transmission for an electric vehicle.
Background
Unlike gasoline vehicles or diesel vehicles using gasoline or diesel, electric vehicles refer to green vehicles that use electricity as a power source so as not to discharge exhaust gas at all.
In the case of a conventional two-stage transmission for an electric vehicle, when a speed is changed from one stage to two stages, a process of forcibly synchronizing the speeds of an input shaft and an output shaft by a synchronizer ring gear or the like is required, and therefore, there is a possibility that a shift shock may occur, and therefore, in order to solve the above problem, higher shift control performance is required. Further, since the transmission for an electric vehicle is driven by an electric drive motor as a vehicle power source, it is required to be light in weight and to have a simpler structure.
Documents of the prior art
Patent document
Patent document 1: korean laid-open patent No. 10-2012-0055335
Disclosure of Invention
The present invention has been made to solve the above-mentioned problems, and an object of the present invention is to provide a two-stage transmission for an electric vehicle, which does not generate a shock when shifting gears, has a compact and simple structure, and can obtain various gear ratios.
The two-stage transmission of the embodiment of the invention includes: a first sun gear; a second sun gear; a plurality of first planetary gears that mesh with the first sun gear to rotate or revolve in a circumferential direction of the first sun gear; a ring gear including an inner peripheral gear and an outer peripheral gear, the outer peripheral gear being engaged with an input gear rotated by a driving device to rotate; a plurality of second planetary gears that are meshed with the inner peripheral gear and the second sun gear and that rotate or revolve in the circumferential direction of the second sun gear; a carrier for rotatably coupling the first planetary gear and the second planetary gear; and a brake unit for selectively fixing the first sun gear and the second sun gear.
The first and second sun gears may include first and second cylindrical extension portions, respectively, the first extension portion having a diameter greater than that of the second extension portion, and the second extension portion may rotate inside the first extension portion.
The above-mentioned brake portion may include: a first brake friction disc and a second brake friction disc which are respectively connected with the first extension part and the second extension part; and a first brake and a second brake for fixing the first brake friction disc and the second brake friction disc, respectively.
The first brake is operated to fix the first sun gear, and the second brake is released to idle the second sun gear, thereby realizing a one-step speed change.
The first brake releases braking to idle the first sun gear, and the second brake operates to fix the second sun gear, thereby realizing a two-stage shift.
The first planetary gear and the second planetary gear are coupled to each other one by one and rotate on a rotation axis provided by the planetary carrier.
The first planetary gear is not meshed with the inner peripheral gear, but is rotatable in the same manner as the second planetary gear in accordance with the rotation of the second planetary gear.
The planet carrier may include an output gear which may mesh with a drive gear.
The planetary carrier may rotate together with the revolution of the first planetary gear or the second planetary gear to output power.
According to the two-stage transmission of the embodiment of the invention, in the case where the gear ratio is modified as needed, it is possible to obtain various gear ratios by changing only the number of teeth of the planetary gear and the sun gear inside the ring gear, so that it is possible to produce a product group of various performances.
Further, in the process of shifting from one stage to two stages and from two stages to one stage, it is not necessary to forcibly make the gear ratio between the input shaft and the output shaft the same, and therefore, no shock occurs at the time of shifting, and it is only necessary to control so that the rotation speed of the idling sun gear becomes 0, and therefore, it is also possible to easily perform the shifting control.
Further, since the two-stage transmission can be configured by 2 planetary gears, 2 brakes, 2 sun gears, and 1 ring gear, the two-stage transmission has a relatively compact and simple structure, and thus, the power of the motor and the efficiency of the battery can be improved by applying the two-stage transmission to an electric vehicle.
Drawings
Fig. 1 is a plan view showing an electric vehicle to which a two-stage transmission according to an embodiment of the present invention is applied.
Fig. 2 is a sectional view of a two-stage transmission for an electric vehicle according to an embodiment of the present invention.
Fig. 3 is a partial sectional view of a two-stage transmission for an electric vehicle according to an embodiment of the present invention.
Fig. 4 is a primary power transmission system diagram of the two speed transmission of the embodiment of the present invention.
FIG. 5 is a diagrammatic view of the two-speed transmission of FIG. 4.
Fig. 6 is a two-stage power transmission system diagram of the two-stage transmission according to the embodiment of the invention.
FIG. 7 is a diagrammatic view of the two-speed transmission of FIG. 6.
Detailed Description
The advantages and features of the present invention and methods of accomplishing the same may be understood more clearly by reference to the following detailed description of embodiments taken in conjunction with the accompanying drawings. However, the present invention is not limited to the embodiments disclosed below, and various forms of the present invention may be embodied, and the present embodiments are provided to make the disclosure of the present invention complete, and to explain the scope of the invention to a person having ordinary skill in the art to which the present invention pertains, and the present invention is defined within the scope of the claims, and the same reference numerals denote the same constituent elements throughout the specification.
The present invention for describing the two-stage transmission 200 for an electric vehicle according to the embodiment of the present invention will be described below with reference to the drawings.
Fig. 1 is a plan view showing an electric vehicle to which a two-stage transmission according to an embodiment of the present invention is applied, fig. 2 is a sectional view of the two-stage transmission according to the embodiment of the present invention, and fig. 3 is a partial sectional view of the two-stage transmission according to the embodiment of the present invention.
Referring to fig. 1 to 3, a two-stage transmission 200 for an electric vehicle according to an embodiment of the present invention includes a first sun gear 210, a second sun gear 220, a ring gear 230, a plurality of first planetary gears 240, a plurality of second planetary gears 250, a carrier 260, and a brake unit.
The ring gear 230 is in a ring shape, and an outer peripheral gear 232 is formed on an outer peripheral surface and an inner peripheral gear 234 is formed on an inner peripheral surface. The outer peripheral gear 232 is engaged with the input gear 120, the input gear 120 is connected to the input shaft 110 rotated by the power of the electrically driven motor 100, and the ring gear 230 rotates at the gear ratio of the input gear 120 to the outer peripheral gear 232 as the input gear 120 rotates. The first and second sun gears 210 and 220 and the first and second planetary gears 240 and 250 are located inside the ring gear 230.
The first sun gear 210 includes a first extension 212 having a cylindrical shape, and an opening hole is formed inside along the axial direction of the cylinder, and is capable of idling or being fixed according to the rotation of the first planetary gear 240. The first extension 212 of the first sun gear 210 extends to protrude outward of the carrier 260.
The second sun gear 220 includes a cylindrical second extension portion 222, and the second sun gear 220 is inserted into the first sun gear 210 and the first extension portion 121, is positioned on the same rotation axis as the first sun gear 210, and is disposed so as to be able to rotate idly in accordance with the rotation of the second planetary gears 250. The diameter of the second sun gear 220 is smaller than the diameter of the first sun gear 210, and the diameter of the second extension 222 is smaller than the diameter of the first extension 212. The second extension portion 222 of the second sun gear 220 is extended to protrude outward of the first extension portion 212 of the first sun gear 210.
The braking portion includes: a first brake disk 214 connected to the first extension 212; a first brake 216 for fixing or rotating the first brake disk 214; a second brake disk 224 connected to the second extension 222; and a second brake 226 for fixing or rotating the second brake disk 224.
The first brake 216 and the second brake 226 are operated or released by an electric motor (not shown), a hydraulic actuator (not shown), or the like, and are used to fix or rotate the first brake friction disk 214 and the second brake friction disk 224, respectively, so that the first sun gear 210 and the second sun gear 220 connected thereto are selectively fixed or rotated, respectively.
The plurality of first planetary gears 240 are engaged with the first sun gear 210 and rotate or revolve around the first sun gear 210 in the circumferential direction.
The plurality of second planetary gears 250 are engaged with the second sun gear 220 and the inner peripheral gear 234, and rotate or revolve around the second sun gear 220 in the circumferential direction.
The first and second planetary gears 240 and 250 are formed of at least 3 planetary gears, and are formed in the same number. The first planetary gears 240 and the second planetary gears 250 are coupled one by one, and when the second planetary gears 250 rotate in accordance with the rotation of the inner peripheral gear 234, the first planetary gears 240 not meshed with the inner peripheral gear 234 also rotate in the same manner as the second planetary gears 250.
The carrier 260 includes an output gear 262 and provides a rotation shaft that can rotate the first planetary gear 240 and the second planetary gear 250. As the first sun gear 210 revolves around the first sun gear 240 or the second sun gear 220 revolves around the second planetary gear 250, the carrier 260 also rotates, and power is transmitted to the drive gear 310 engaged with the output gear 262 via the output gear 262.
As the drive gear 310 rotates, the power of the motor 100 is transmitted to the differential device 300, and is transmitted to tires (not shown) through drive shafts 320 and 330 disposed on both sides of the differential device 300.
So far, additional explanation is omitted, but the respective components of the two-stage transmission are supported or rotated by a plurality of bearings.
Referring to fig. 4 to 7, the shifting operation of the two-stage transmission 200 according to the embodiment of the present invention will be described in detail.
Fig. 4 is a primary power transmission system diagram of the two speed transmission of the embodiment of the present invention. FIG. 5 is a diagrammatic view of the two-speed transmission of FIG. 4. Fig. 6 is a two-stage power transmission system diagram of the two-stage transmission according to the embodiment of the invention. FIG. 7 is a diagrammatic view of the two-speed transmission of FIG. 6.
First, in a gear-neutral state, when the first brake disk 214 and the second brake disk 224 are not fixed to the first brake 216 and the second brake 226, respectively, and the first brake disk 214 and the second brake disk 224 are allowed to automatically rotate idly, the first sun gear 210 and the second sun gear 220 are allowed to freely rotate idly if the first brake disk 214 and the second brake disk 224 are allowed to freely rotate idly.
As the motor 100 rotates, the outer peripheral gear 232 rotates, and even if the second planetary gear 250 also rotates via the inner peripheral gear 234, the second planetary gear 250 rotates around the rotation shaft of the planetary carrier 260, rather than revolving around in the circumferential direction of the second sun gear 220. That is, since the carrier 260 receives a large force by the ground contact force of the tire, the second sun gear 220 idles with the rotation of the second planetary gears 250.
Further, the first planetary gear 240 rotates with the rotation of the second planetary gear 250, and the first sun gear 210 idles with the rotation of the first planetary gear 240 without revolving in the circumferential direction of the first sun gear 210 for the same reason as described above.
Next, as shown in fig. 4 and 5, the two-stage transmission 200 according to the embodiment of the present invention is observed in a state of shifting to one stage. In one stage, the first brake 216 operates to fix the first brake disk 214, and the second brake 226 releases the brake, so that the second brake disk 224 can be idly rotated.
Therefore, as the input gear 120 rotates, the outer peripheral gear 232 rotates, and thereby the second planetary gear 250 rotates. Also, the second sun gear 220 can be idly rotated, and thus, even if the second planetary gears 250 are rotated, the second sun gear 220 is idly rotated.
On the other hand, as the second sun gear 250 rotates, the first planetary gears 240 also rotate, and the first sun gear 210 is fixed, so the first planetary gears 240 revolve along the circumferential direction of the first sun gear 210, and therefore the carrier 260 also rotates along with the revolution of the first planetary gears 240, and the one-stage gear shift is completed. The first gear ratio is determined according to the number of teeth of the first planetary gears 240 and the first sun gear 210.
Next, as shown in fig. 6 and 7, the two-stage transmission 200 according to the embodiment of the present invention is observed to perform a two-stage shift. In the second stage, the second brake 226 is operated to fix the second brake disk 224, and the first brake 216 releases the brake, so that the first brake disk 214 can be idly rotated.
Therefore, as the input gear 120 rotates, the outer peripheral gear 232 rotates, and thereby the second planetary gear 250 rotates. Since the second sun gear 220 is fixed, the second planetary gears 250 revolve along the circumferential direction of the second sun gear 220, and the carrier 260 also rotates along with the revolution of the second planetary gears 250, thereby completing the two-stage gear shift. The two-stage gear ratio is determined according to the number of teeth formed on the second planetary gears 250 and the second sun gear 220.
On the other hand, as the second planetary gears 250 rotate, the first planetary gears 240 rotate, and the first sun gear 210 may be idly rotated, and thus, even if the first planetary gears 240 rotate, the first sun gear 210 is idly rotated.
When the gear is shifted from the first stage to the second stage, the first brake 216 immediately releases the brake, and the second brake 226 may be controlled so that the second sun gear 220 that idles is fixed, that is, so that the number of revolutions of the second sun gear 220 becomes 0.
On the other hand, when the gear is shifted from the second stage to the first stage, the second brake 226 immediately releases the brake, and the first brake 216 may be controlled so that the idling first sun gear 210 is fixed, that is, so that the number of revolutions of the first sun gear 210 becomes 0.
As described above, when the speed is changed from one stage to two stages or from two stages to one stage, since there is no need to forcibly synchronize the speeds by a synchronizer ring or the like in order to reduce the speed difference between the input shaft and the output shaft, the speed change control can be easily performed because the speed change shock does not occur and the number of revolutions of the first sun gear 210 or the second sun gear 220 that is idling is controlled to be 0.
Also, the two-stage transmission 200 of the embodiment of the invention can obtain various gear ratios by adjusting the number of teeth of the first planetary gears 240 and the first sun gear 210 and the number of teeth of the second planetary gears 250 and the second sun gear 220.
Further, the two-stage transmission 200 according to the embodiment of the present invention can be configured to have a relatively compact and simple structure by using 2 planetary gears, 2 brakes, 2 sun gears, and 1 ring gear, and thus can improve the power of the motor and the efficiency of the battery by applying it to an electric vehicle.
The two-stage transmission 200 according to the embodiment of the present invention is applied to an electric vehicle driven by the motor 100, but may be applied to a vehicle driven by an internal combustion engine other than the motor 100.
The embodiments of the present invention have been described above, but the scope of the invention claimed is not limited thereto, and includes all changes and modifications that can be recognized as equivalent scope by a person of ordinary skill in the art from the embodiments of the present invention through simple modifications.

Claims (7)

1. A two-stage transmission characterized in that,
the method comprises the following steps:
a first sun gear;
a second sun gear;
a plurality of first planetary gears that mesh with the first sun gear to rotate or revolve in a circumferential direction of the first sun gear;
a ring gear including an inner peripheral gear and an outer peripheral gear, the outer peripheral gear being engaged with an input gear rotated by a driving device to rotate;
a plurality of second planetary gears that are meshed with the inner peripheral gear and the second sun gear and that rotate or revolve in the circumferential direction of the second sun gear;
a carrier for rotatably coupling the first planetary gear and the second planetary gear; and
a brake part for selectively fixing the first sun gear and the second sun gear,
the first and second sun gears include cylindrical first and second extending portions, respectively, the first extending portion having a diameter larger than that of the second extending portion, the second extending portion rotating inside the first extending portion,
the braking portion includes:
a first brake friction disc and a second brake friction disc which are respectively connected with the first extension part and the second extension part; and
and the first brake and the second brake are respectively used for fixing the first brake friction disc and the second brake friction disc.
2. The two-stage transmission according to claim 1, wherein the first brake is operated to fix the first sun gear, and the second brake is released to idle the second sun gear, thereby realizing a one-stage speed change.
3. The two-stage transmission according to claim 1, wherein the first brake releases braking to idle the first sun gear, and the second brake operates to fix the second sun gear, thereby realizing a two-stage shift.
4. The two-stage transmission according to claim 1, wherein the first planetary gear and the second planetary gear are coupled to each other one by one and rotate on a rotation shaft provided by the carrier.
5. The two-stage transmission according to claim 1, wherein the first planetary gear does not mesh with the inner peripheral gear but rotates in the same manner as the second planetary gear according to the rotation of the second planetary gear.
6. The two speed transmission of claim 1, wherein the planet carrier includes an output gear, the output gear meshing with a drive gear.
7. The two-stage transmission of claim 1, wherein the carrier rotates in unison with the revolution of the first planetary gear or the second planetary gear to output power.
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US10480622B2 (en) 2019-11-19
US20180216709A1 (en) 2018-08-02

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